Variable speed linkage



Aug- 2, 1966 w. WELLSTEIN 3,263,511

VARIABLE SPEED vI INKAGE Filed Deo. 2, 1963 l L l-@ 57 1NVENTOR WILLIAMwELLsTEl United States Patent O "ice 3,263,511 VARIABLE SPEED LINKAGEWilliam Wellstein, Fostoria, Ohio, assigner, by mesne assignments, toKerco, Inc., a. corporation of Delaware Filed Dec. 2, 1963, Ser. No.327,358 Claims. (Cl. 74--53) The present invention relates toimprovements in a linkage for the operati-0n of various types ofequipment at variable speeds froma single power source. As an example,the improved linkage may be employed to great advantage in controllingthe travel of a tool or work carrying slide in reversing strokes underactuation by a single operating cam. More particularly, the controlfunction is performed through the agency of novel dual type bell crankand lever linkage |provisions enabling a multiplication of lever `armratios through such linkage which can produce a vast and widely variablemodification of the speed or power of an actuating stroke, applied bythe linkage to a tool slide or the like, in relation to the strokeapplied to the linkage by a cam or like pri mary actuator.

In general, it is an object of the invention to provide an improved,variable speed tool slide or equivalent actuating linkage driven from asingle master power member, which is capable of providing a wide rangeof ratios of power cam throw, or stroke or throw of an equivalentoperator, to slide stroke distance.

Another object is to provide an improved slide or equivalent unitoperated by means of such improved linkage. The unit operated by t-helinkage might, for example, be a slide mounting a grinding, drilling orlike head for variable speed movements, such as approach, working andretract travel componen-ts, relative to the work, or mou-nting aworkpiece for variable movement in relation to a tool, or for a moregeneral type of travel for whatever particular purpose Vmay be involved.

More specifically, the improved linkage comprises Ia primary actuator ormedially pivoted bell crank and a coacting secondary actuator lever orarm member. In this arrangement, the bell crank, as directly engaged andoperated at one of its arms by a master cam, affords a given ratio ofthe radial cam throw of that arm to the length of stroke of the slide,as the latter is directly engaged by the other arm of the bell crank.This may be employed, for example, `to afford a relatively fast initialadvance and final subsequent retraction of a tool on the slide towardand away from a workpiece prior to and following Ian actual workingphase.

The linkage combines with a bell crank -having this effect a mediallypivoted secondary lever or arm member, one end of which :is engaged byan element of the bell crank on the side of the latters pivot oppositeits slide engaging end. Thus the distance of this bell crank elementfrom the bell crank pivot represents a further moment advantage anm ofsmall length through which the medially pivoted lever or arm member isbell-crank actuated.

The product of the combination of crank and lever ratios represents lavery high cam throw-slide str-oke ratio, indeed, so that with theopposite end of the medially pivoted lever directly engaged with thetool slide, like the bell crank but independently of the latter, thereresults a slow feed of the tool in the actual working phase of theequipment. In accordance with the invention, the last named productratio is capable vof a wide range of change by an apt `selection of:bell crank and lever components and an adjustment of their points ofengagement with one another.

It is of course to be kept in mind that the improved linkage is welladapted to applications other than tool 3,263,51 l Patented August 2,1966 slide control; however, that application typically illustrates theadvantages of the linkage, and will therefore be alone referred to inthe following description.

Thus, with the bell crank and medially pivoted arm journaled onindependent axes determining the length ratios of their respective arms,and with these members physically acting independently upon the toolslide, but co-ordinately in at least one of its travel phases, the slidemay have a fast initial inward movement from -a fully retracted positionto the point of engagement of the tool with the work, followed byretarded ensuing movement toward and into the workpiece, then byrelatively slow and rapid retractions of vthe slide after the workingphase.

In further accordance with the invention, there is provided anadjustability as to the point of engagement of the bell crank with themedially pivoted, secondary lever or arm, thus permitting a `full rangeof intermediate ultimate ratios of cam throw to slide stroke. Let it beassumed, as -herein shown and described, that the bell crank engages thelonger of two arm portions of the secondary lever at a relatively shortdistance from the bell crank pivot, and only a small fraction of thelength of the cam-engaging bell crank anm. Then, for example,appropriate selection of the length of bell crank arms and pivoted armportions will enable a full slide stroke of 0.003 inch when the ultimateratio is 1:10, a stroke of 0.015 inch at 1:20 ratio, etc.; and anappropriate small adjustment at the point of operating engagement of thebell crank and lever arm will have the effect of selecting anintermediate ratio, such as 1:15.75 or thereabouts, A greater adjustmentof the distance from the engagement point to the bell crank axis willresult in a greater modification of the ratio, for example, halving ordoubling it.

Thus the invention features simple linkage provisions enabling a widerange of control of the stroke of a movable tool slide or other variablestroke member, which were, for instance, -heretofore only -attainedthrough resort to the use of multiple interchangeable cams or liketime-consuming practice, such as is rendered unnecessary by the improvedsingle cam-controlled linkage of the invention.

A general object of the invention is to provide a variable speedoperating linkage fora slide or the like, characterized in that thelinkage imparts successively to the slide an initial advance stroke inone direction under the sole control of the bell crank of the linkage, ashort inward working component under the combined control 0f the bellcrank and lever at a highly increased stroke speed reduction ratio,followed by a retract component in the opposite direction at increasedspeed, again under the control of the bell crank of the linkage; and inwhich the transisitions as between these speed components areaccomplished smoothly and without 4any degree of jarring. The inventionalso contemplates adjustable provisions whereby the point of .take-overmay be determined as desired for slide strokes of different speedcharacteristics.

The foregoing as well as other objects will become more apparent as thisdescription proceeds, especially when considered in connection with theaccompanying drawings illustrating the invention, wherein:

FIG. 1 is a fragmentary perspective and quite schematic view of aportion of typical tool slide equipment in which the linkage of theinvention may be incorporated, other components of this equipment havingbeen omitted as not germane to the invention;

FIG. 2 is a fragmentary view in vertical section through the slide andassociated linkage of the machine, showing the dual bell crank and armof the linkage as operated by a master cam;

FIG. 3 is an end view of components of the linkage alone, as viewed fromthe left of FIG. 2;

FIG. 4 is a fragmentary view, partially broken away and in horizontalsection on line 4-4 of FIG. 3; and

FIG. 5 is a highly schematic diagram illustrating the nature of theadvance, working and retract strokes imparted to the slide by theimproved linkage.

Referring to FIG. 1, the generally known type of machine shown thereinto which the improved linkage is applied may be considered to comprisean appropriate rigid base 11 having a horizontal top 12 upon which amounting slide 13 is guided for longitudinal reversing movement. Eachslide is adapted to have mounted thereon an appropriate tool head (notshown). F-urther reference to the nature of the slide 13 will be made.The improved linkage of the invention is generally designated by thereference numeral 30.

Referring now particularly to FIG. 2, the machine top 12 fxedly mounts aguide or Way member 32 for the slide 13, by which the latter is stablyguided in its strokes to the right and left as viewed in FIG. 2. A smallblock 33 is xed to the bottom of slide 13 to depend within an elongatedrecess 34 of guide member 32; and an elongated adjusting stud or stem 35is threaded through block 33, extending outwardly through guide member32 and a depending end cover plate 36 on the slide. Stem 35 has aknurled handpiece 37 secured thereon outwardly of element 36, and thehandpiece may be appropriately calibrated as shown in FIG. 1, tovisually indicate the position of threaded adjustment of the stud orstern 35 longitudinally relative to the tool slide 13. The stem 35 isadapted to be actuated by a part of the linkage 30, as will bedescribed.

A tension coil spring 38 has one end secured to the end plate element 36of slide 13 and the other end connected to frame 11, thus urging .theslide to the right, as viewed in FIG. 2, for its in-stroke.

The block 33 also receives another, set screw type adjusting stem 39shown along with stem or stud 35 in dot-dash line in FIG. 3. The stem 39serves as an actuator for another component of linkage 30, as will alsoappear later.

Now referring to FIGS. 2, 3 and 4, a bell crank member of the linkage 30is generally designated 40, comprising an upright slide operating arm 41and an inclined though generally horizontal operated aum 42. The arm 42is provided at its end with a follower roller 43 engageable with adriven faster cam 44, against which it is urged by an appropriatelyanchored tension spring 42'; while the arm 41 is provided with -a sideboss 45 apertured and receiving a bushing 46, at which the bell crank ispivoted on a horizontal pin 47 fixedly carried by a bracket 48 on theouter side of the machine frame 11. It is seen by reference to FIG. 2that the bell crank 40 is thus pivoted on the frame 11 at a pointslightly above the junction of bell crank arms 41 .and 42; and one ofthe moment arms of the lbell crank is established by this positionalrelationship, as will be described.

At its top end, the bell crank arm 41 is provided with an anti-frictionroller 50 ladapted for engagement with the adjustable set screw 39 onslide block 33. Arm 41 also carries, adjacent the pivot bracket 48, alaterally projecting rectangular pad 52 which is provided with anelongated Iupright slot 53 for a purpose to be described. The arm 42 ofbell crank 40 extends inwardly through an opening 54 of frame 11 forengagement with master cam 44.

While the cam 44 is shown as the primary power member for the input ofenergy to linkage 30, it will be understood that the inventioncontemplates as an equivalent any other suitable, identically repeatingor cycling power unit which is capable of periodically imparting apredetermined throw to the bell crank arm 42, or equivalent memberoperated by such power unit, hence is capable of automatically repeatingthe variable speed operating strokes contemplated by the invention, `fora given setting of linkage 30.

The second component of the linkage 30 is a secondary actuator, armmember or rocker lever, generally designated 56, which is mediallyprovided with a boss 56 at which it is pivoted by a pin 57 in a bracket58 secured to and projecting from the exterior of frame 11, with abushing 59 in the arm boss 56 receiving pin 57. A slide operatingportion 60 of arm 56 above its pivot 57 is provided with ananti-friction roller 61, which is in side-byside -relation to the roller50 atop the bell crank arm 41, as shown in FIGS. 3 and 4. The roller 61is engageable in operation by the end of adjusting stud or stem 35.

The lower, operated portion `63 of the medially pivoted arm 56 isprovided with a lateral extension piece 64; and in accordance with theinvention, this extension 64 is engageable lby an actuator stud 65 whichextends through the slot 53 of bell crank pad 52, being provided withlock nuts 66, l67 on opposite sides of the pad. This enables the stud 65to be adjusted as desired up and down in the slot 53, then clamped toconstitute a lever actuating element of the bell crank 40, the primaryactuator of linkage 30. The position of stud 65 determines its distancefrom the pivotal axis of bell crank 40 at pin 47, which distancerepresents the moment arm (hereinafter referred to) about which the bellcrank acts on the lever 56 at the latters extension 64.

Thus, reference being had to FIG. 3 of the drawings, it is seen that thedistance x of actuator stud 65 from the bell crank pivot at -pin 47represents a very short moment or lever arm of the bell crank 40, ascompared with its long arm distance y from pivot 47 to follower 43. Theratio xzy of effective lengths may be, for example, 1:10 in a typicalinstallation, and is a multiplier by which the ultimate combined, motiondropping ratio of linkage 30 is determined. The selection of a bellcrank having, as between its pivot and its cam and slide ends, adifferent lever arm or moment ratio will of course vary the combinedratio, enabling it possibly, by choice of bell cranks, to provide anextremely wide range of slide stroke lengths.

The medially pivoted, secondary lever 56 of linkage 30 has a moment arma from its pivot at 57 to its anti-friction roller 61 and a moment arm bfrom its pivot to its point of effective engagement by primary bellcrank 40 at the actuator stud member 65. For example, the ratio a/b maybe about 1/2 in a typical linkage, so if x/y equals about 1/10, theoverall motion conversion ratio of the linkage 30 is about 1:20, i.e., acontrolled working motion of the slide 13 where its adjustable stud 35engages the anti-friction roller 60 of lever 56 amounting to one unit oflength for 20 units of radial throw by master cam 44, the basic driverfor the linkage. This affords a slow in and out feed of slide 13 in aworking engagement of its tool (not shown) with a workpiece.

On the other hand, there is available a rapid speed advance and retractof slide 13, as effected only by and at the engagement of set screwstern 39 with the bell crank anti-friction roller 50, in a much greaterratio of, say, approximately 1:2, for rapid in and out initial and finalstrokes of a slide cycle, amounting to one length unit of slide travelto only about two radial throw units of cam 44.

As an instance of the adjustability of the linkage at the actuator stud65, let it be assumed that the latter is set on pad 52 at a distance xof 1.3 inches from the bell crank pivot axis at pin 47, that theeffective bell crank arm length from pivot to follower 43 is 13 inches,and that the lever arm lengths a and b are 2.6 inches and 5.2 inchesrespectively. Then, stated inversely, the combined ratio of linkage 30is However, if actuator stud 65 is adjusted only one inch down on pad52, the arm x becomes 2.3", the arm b becomes 6.2", and the combinedratio equals or 13.47z1. Thus in the first case there is, in a givenrange broadly determined by bell crank and lever design, a twenty-folddrop in slide travel, and in the other case a drop of approximatelythirteen and a 'half to one.

A wide selection of slide operating ratios is available, along with afine control in any general range, as determined by the adjustment ofbell crank actuator stud 65. For instance, the adjustment may result inthe multiplying or dividing of the moment arm length x to producedifferent orders of ultimate stroke ratio; and an intermediate fineadjustment may be had in any general order or range of adjustment. It iscontemplated that the pad 52 of the bell crank may be calibratedadjacent the stud slot to assist in making the desired setting (FIG. 3).The invention contemplates a selection and adjustment of linkage 30, inregard to moment arm lengths of bell crank and/ or lever, such as willpermit combined linkage ratios ranging from :1 (representing an overallslide stroke of, say, 0.003 inch) to :1 (or a 0.00375 inch stroke).

In operation, assuming that the tool slide 13 is in an extreme withdrawninitial position to the left in FIG. 2,

with the follower 43 of -bell crank 40 riding a high of master cam 44,the set screw actuator 39 on the slides block 33 will then be inengagement with the anti-friction roller of bell crank arm 41. Asfollower 43 rides onto a low (not shown) of cam 44, the bell crank 40swings clockwise about its pivot pin 47, enabling bell crank roller 50to fall inwardly, or to the right in FIG. 2; and the medially pivotedsecondary lever 56 follows in the same direction. Thus a rapid instrokeof slide 13 and its tool into initial engagement of the latter with aworkpiece takes place under the urging of slide spring 38.

Upon the wheels assuming such workpiece engagement, with the extension64 of lever arm 63 engaged by bell crank actuator stud 65, the motion ofslide 13 cornes under the control of the combined linkage 30. The slidecontinues to be spring-urged inwardly for the working phase of itsstroke, as variably controlled by the contour of master cam 44, but atone of the combined higher ratios discussed above, i.e., at a greatlydiminished rate of travel.

As the slide completes this stroke phase, the follower 43 will beactuated by a cam high (not shown) for an outward throw, rocking bellcrank 40 counterclockwise about its pivot pin 47. The resultant initialretraction of the slide and wheel from the work will first be at theslower rate, until the bell crank roller 50 moves to the rear away fromlever roller 61, whereupon the slide 13 will be retracted at the bellcranks 2:1 throw ratio until slide 13 is fully withdrawn outwardly, thesecondary lever 56 following at the slower ratio rate.

Schematic FIG. 5 conveniently illustrates the characteristics of thevariable speed stroke imparted to slide 13 by the linkage. The bellcrank 40 will, at the operating engagement of its roller 50 with theadjustment set screw 39, describe a stroke arc A extending equidistantlyon opposite sides of an upright center line through the roller, thepivot axis at 57 for secondary lever 56 and the point of engagement ofactuator stud with the lever extension 64. However, only the componentof the stroke arm A which lies to the left of the center line isdirectly and alone effective on slide 13, producing its rapid initialinward component and its rapid final outward component.

As the bell crank arrives at the stroke center line, having effected acoarse slide control movement to approach a tool or the like thereon toclose proximity to a workpiece, for example, the fine, high ratiocontrol comes into effect, as exerted by the engagement of the roller 61on lever 56 with the adjustment stud or stem 35. The Vduration of thisis only to the slight extent of the stroke arc A which lies to the rightof the center arm, both on the infeed and outfeed directions of slidemovement. In this phase, a tool will -be in working engagement with thework.

When the lever 56 is returned to the upright center line, it losescontrol effect on the slide 13, which is taken up by the bell crank forthe remainder of the retract stroke, on the left of the center line. Allof these transitions are effected smoothly and without shock or jarring;and the point of cross-over from one phase to another may be varied byan appropriate adjustment of the adjustment stud 35.

It is seen that the invention affords a highly versatile slide controlmechanism. A single, dual-type bell crank and lever linkage, which ishighly compact, simple and inexpensive, and readily adaptable to varioussorts of existing machinery, permits changeovers vas to slide strokeratio in a moments time and without any change whatsoever in theequipment other than in making the adjustment as to bell crank momentarm distance. Such changeovers have heretofore been accomplished only bytime-consuming modifications of the equipment. In so far as the matterof stroke accuracy is concerned, the present linkage, as actuated at alltimes from a single master power input member or cam, is of course atleast the equivalent of any heretofore relied on procedure.

As indicated above, the master power source may be a driven cam or vanyother equivalent agency capable of producing the bell crank throw.Furthermore, while the illustrated embodiment of the invention has itsoperating slide 13 spring-urged in one direction, and actuated in theother direction by the linkage 30, `it is to be understood that otheroperating means for the slide, acting in conjunction with the linkage,such as fluid pressure or mechanical operating means, are contemplated.

`What I claim as my invention is:

1. In apparatus of the type described, a support, a slide unit mountedfor reversing sliding movement on said support, a linkage to operatesaid slide unit at varying speeds in different phases of said movement,said linkage comprising a primary actuator operatively engaging saidunit, said actuator having a pivotal axis on said support and having afirst portion to engage and operate said unit at a given speed in one ofsaid phases, and a second operated portion to `be operated, a secondaryactuator operatively engaging said slide unit and having a -pivotal axison said support in parallel but transversely spaced relation to thepivotal axis of said primary actuator, said secondary actuator alsohaving a portion to engage and operate said unit and a further portionproviding an operating connection for actuation by said primaryactuator, which further portion is transversely spaced from the pivotalaxis of the primary actuator, the moment arm distance from said primaryactuator axis to said further portion being substantially dilferent fromthe distance from said primary actuator axis to its said second operatedportion, said actuators thus coacting in yoperating the slide unit at adifferent speed in another of said phases, and an automatically cyclingdrive device engaging said primary actuator at said second operatedportion of the latter to provide repeated variable speed movement of theslide unit over the direction of the two phases.

2. A linkage to operate a unit at varying speed in different phases ofits movement, said linkage comprising a primary actuator operativelyengaging said unit, said actuator having a pivotal axis and having afirst portion to engage ,and operate said unit at a given speed in oneof said phases, and a second operated portion adapted to be operated byother means, a secondary actuator operatively engaging said unit andhaving a pivotal axis in parallel but transversely spaced relation tothe pivotal axis of said primary actuator, said `secondary actuatorhaving a portion to engage and operate said unit and a further portionlproviding an operating connection for actuation by said primaryactuator, which further portion is transversely spaced from the pivotalaxis of the primary actuator, the moment arm distance from said primaryactuator axis to said further portion being substantially differentfrom, and in a predetermined and fixed ratio to, the moment arm distancefrom said primary actuator axis to its said second operated portion,said actuators thus coacting in operating the unit at a different speedin another of said phases, and means to adjust the ratio of the lengthsof said moment arm distances to one another.

3. In apparatus of the type described, a support, a slide unit mountedfor reversing sliding movement on said support, and a linkage to operatesaid slide unit at varying speeds in different phases of said movement,said linkage comprising a primary actuator operatively engaging saidunit, said actuator having a pivotal axis on said support and having afirst portion to engage and operate said unit at a given speed in one ofsaid phases, and a second operated portion adapted to be operated byother means, a secondary actuator operatively engaging said slide unitand having a pivotal axis on said support in parallel but transverselyspaced relation to the pivotal axis of said primary actuator, saidsecondary actuator also having a portion to engage and operate said unitand a further portion providing an operating connection for actuation bysaid primary actuator, which further portion is transversely spaced fromthe pivotal axis of the primary actuator, the moment arm distance fromsaid primary actuator axis to said further portion being substantiallydifferent from the distance from said primary actuator axis to its saidsecond operated portion, said secondary actuator providing moment armsfrom the axis thereof which are of different lengths, respectively, tosaid further portion and to said first named unit operating portion ofthe secondary actuator, said actuator thus coacting in operating theslide unit at a different speed in another of said phases, said firstactuator being a bell crank medially pivoted between said operating andoperated portions thereof, said secondary actuator being a mediallypivoted lever.

4. Apparatus in accordance with claim 3, in which said operatingconnection between said actuators is located on the same side of both ofsaid pivotal axes and closer to the bell crank axis than to the leveraxis, and means to adjust the moment arm distance from the axis of saidlever to said further portion thereof.

5. A linkage to operate a unit as varying speeds in different phases ofits movement, said linkage comprising a primary actuator operativelyengaging said unit, said actuator having a pivotal axis and having afirst portion to engage and operate said unit at a given speed in one ofsaid phases, and a second operated portion adapted to be operated byother means, a secondary actuator operatively engaging said unit andhaving a pivotal axis in parallel but transversely spaced relation tothe pivotal axis of said primary actuator, said secondary actuatorhaving a portion to engage and operate said unit and a further portionproviding an operating connection for actuation by said primaryactuator, which further portion is transversely spaced from the pivotalaxis of the primary actuator, the moment arm distance from said primaryactuator axis to said further portion being substantially, differentfrom, and in a predetermined and fixed ratio to, the distance from saidprimary actuator axis to its said second operated portion, saidsecondary actuator providing moment arms from the axis thereof which areof different lengths, respectively, to said further portion and to saidfirst named unit operating portion of the secondary actuator, saidactuators thus coacting in operating the unit at a different speed inanother of said phases, said first actuator being a bell crank mediallypivoted between said operating and -operated portions thereof, saidsecondary actuator being a medially pivoted lever.

6. A linkage in accordance with claim S, in which the distance from saidoperated portion to the bell crank axis greatly exceeds the moment armdistance from said bell crank axis to said operating connection, thedistance from the medial axis of said pivoted lever to said furtherportion thereof substantially exceeding the distance from said medialaxis to said first named unit operating portion of said lever.

7. A linkage in accordance with claim 5, and further comprising means toadjust said moment arm distance from the axis of said lever to saidfurther portion thereof.

8. A linkage in accordance with claim 6, and further comprising means toadjust said moment arm distance from the axis of said lever to saidfurther portion thereof.

9. A linkage in accordance with claim 8, in which said operatingconnection between said actuators is located on the same side of both ofsaid pivotal axes.

10. In apparatus of the type described, a support, a slide unit mountedfor reversing sliding movement on said support, a linkage to operatesaid slide unit at varying speeds in different phases of said movement,said linkage comprising a primary actuator operatively engaging saidunit, said actuator having a pivotal axis on said support and having afirst portion to engage and operate said unit at a given speed in one ofsaid phases, and a second operated portion to be operated, a secondaryactuator operatively engaging said slide unit and having a pivotal axison said support in parallel but transversely spaced relation to thepivotal axis of said primary actuator, said secondary actuator alsohaving a portion to engage and operate said unit and a further portionproviding an operating connection for actuation by said primaryactuator, which further portion is transversely spaced from the pivotalaxis of the primary actuator, the moment arm distance from said primaryactuator axis to said further portion being substantially different fromthe distance from said primary actuator axis to its said second operatedportion, said secondary actuator providing moment arms from the axisthereof which are of different lengths, respectively, to said furtherportion and to said rst named unit operating portion of the secondaryactuator, said actuators thus coacting in operating the slide unit at adifferent speed in another of said phases, and an automatically cyclingdrive device engaging said primary actuator at said second operatedportion of the latter to provide repeated variable speed movement of theslide unit over the duration of the two phases.

11. In apparatus of the type described, a support, a slide mounted forreversing movement on said support, and a linkage to operate said slideat widely varying speeds in different phases of said movement, saidlinkage comprising a primary actuator pivoted on an axis on said supportand having operated and operating arms respectively engaging andoperated by a driving member and engaging and directly operating saidslide in one phase of its movement, a secondary actuator having a pivotaxis on said support in parallel but transversely spaced relation to thepivot axis of said primary actuator on the support, said secondaryactuator having direct operating engagement with said slide to operatethe latter in a different phase of its movement and being provided withmeans for an operating connection for actuation by said primary actuatorat a point transversely spaced from the pivot axis of the latter, themoment arm distance from said primary actuator pivot axis to saidoperating connection being substantially different from that from saidactuator axis to the point of engagement of said operated arm of theprimary actuator with said driving member, said secondary actuatorproviding moment arms which are of different lengths, respectively, tosaid operating connection and to the point of operating engagement ofsaid secondary actuator with said slide, the slide being therebyoperable by the linkage in said dif-ferent phase of a stroke of saidslide at a speed determined by the product of the respective moment armratios of said actuators.

12. In apparatus of the type described, a support, a slide mounted forreversing movement on said support, and a linkage to operate said slideat widely varying speeds in different phases of said movement, saidlinkage comprising a primary actuator pivoted on an axis on said supportand having operated and operating arms respectively engaging andoperated by a driving member and engaging and directly operating saidslide in one phase of its movement, a secondary actuator having a pivotaxis on said support in parallel but transversely spaced relation to thepivot axis of said primary actuator on the support, said secondaryactuator having direct operating engagement with said slide to operatethe latter in a different phase of its movement and being provided withmeans for an operating connection for actuation by said primary.actuator at a point transversely spaced from the pivot axis of thelatter, the moment arm distance from said primary actuator pivot axis tosaid operating connection being substantially different from that fromsaid actuator axis to the point of engagement of said operated arm ofthe primary actuator With said driving member, said secondary actuatorproviding moment arms Which are of different lengths, respectively, tosaid operating connection and to the point of operating engagement ofsaid secondary actuator with said slide, the slide being therebyoperable by the linkage in said dilerent phase of a stroke of said slideat a speed determined by the product of the respective moment arm ratiosof said actuators, and means to adjust said operating connection towardand away from said pivot axis of said primary actuator.

13. In apparatus of the type described, a support, a slide mounted forreversing movement on said support, and a linkage to operate said slideat Widely varying speeds in different phases of said movement, saidlinkage comprising a bell crank medially pivoted on an axis on saidsupport and having operated and operating arms respectviely engaging andoperated by a driving member and engaging and directly operating saidslide in one phase of its movement, the length of the operated arm beinggreater in the degree of a substantial multiple of that of the operatingarm, a lever having a pivot axis intermediate its length on said supportin parallel but transversely `spaced relation to the pivot axis of saidbell crank on the support, said lever having direct operating engagementat one end with said slide to operate the latter in a different phase ofits movement and being provided adjacent its other end With an operatingconnection for actuation by said bell crank at a point transverselyspaced from the pivot axis of the latter, said other end of said leverbeing at a side of said bell crank axis remote from the lever axis, themoment arm distance from said bell crank axis to said operatingconnection being substantially less than that from said bell crank axisto the point of engagement of said operated arm of the bell crank tosaid driving member, said lever providing moment arms on oppositesidesof its pivot axis which are of greater and lesser lengths,respectively, to said operating connection and to the point of leveroperating engagement with said slide, the slide being thereby operableby the linkage in said dierent phase of a stroke of said slide at aspeed determined by the product of the respective moment arm ratios of`said bell crank and lever.

14. In apparatus of the type described, a support, a slide mounted forreversing movement on said support, and a linkage to operate said slideat Widely varying speeds in different phases of said movement, saidlinkage comprising a bell crank medially pivoted on an axis on saidsupport and having operated and operating arms respectively engaging andoperated by a driving member and engaging and directly operating saidslide in one phase of its movement, the length of the operated arm beinggreater in the degree of a substantial multiple of that of the operatingarm, a lever having a pivot axis intermediate its length on said supportin paralllel but transversely spaced relation to the pivot axis of saidbell crank on the support, said lever having direct operating engagementat one end with said slide to operate the latter in a different phase ofits movement and being provided adjacent its other end with an operatingconnection for actuation by said bell crank at a point transverselyspaced from the pivot axis of the latter, said other end of said leverbeing at a side of said bell crank axis remote from the lever axis, themoment arm distance from said bell crank axis to said operatingconnection being substantially less than that from said bell crank axisto the point of engagement of said operated arm of the bell crank tosaid driving member, said lever providing moment arms on opposite sidesof its pivot axis which are of greater and lesser lengths, respectively,to said operating connection and to the point of lever operatingengagement With said slide, the slide being thereby operable by thelinkage in said dilerent phase of a stroke of said slide at a speeddetermined by the product of the respective moment arm ratios of saidbell crank and lever, and means to adjust said operating connectiontoward and away from the bell crank axis.

15. A linkage to operate a unit at varying speeds in different phases ofits movement, said linkage comprising a primary actuator operativelyengaging said unit, said actuator having a pivotal axis and having alirst portion to engage and operate said unit at a given speed in one ofsaid phases, and a second operated portion adapted to be operated byother means, a secondary actuator operatively engaging said unit andhaving a pivotal axis in parallel but transversely spaced relation tothe pivotal axis of said primary actuator, said secondary actuatorhaving a portion to engage and operate said unit and a further portionproviding an operating connection for actuation by said primaryactuator, which further portion is transversely spaced from the pivotalaxis of the primary actuator, the moment arm distance from said primaryactuator axis to said further portion being substantially differentfrom, and in a predetermined and fixed ratio to, the moment arm distancefrom said primary actuator axis to its said second operated portion,said secondary actuator providing moment arms from the axis thereofwhich are of different lengths, respectively, to said further portionand to said first named, unit operating portion of the secondaryactuator, said actuators thus coacting in operating the unit at adifferent speed in another of said phases, and means to adjust the ratioof the lengths of said moment arm distances to one another.

References Cited by the Examiner UNITED STATES PATENTS 1,117,661 11/1914Gourlay 74-101 1,853,495 4/ 1932 Bertrand 74--518 1,934,456 11/1933Taylor 74-516 2,005,019 6/1935 Bertrand 74-518 2,43 6,897 3/1948 Nutt74-5l6 2,690,321 9/1954 Luna et al 74-516 X 2,809,725 l0/ 1957 Ayers74-516 X 2,909,936 10/1959 Huthsing et al 74-102 MILTON KAUFMAN, PrimaryExaminer.

BROUGl-ITON G. DURHAM, D. H. THIEL,

Assistant Examiners.

UNITED STATES PATENT OFFICE CERTIFICATE OF CQRRECTION Patent No. 3 263,Sll August Z 1966 William Wellstein It is hereby certified that errorappears in the above numbered patent requiring Correction and that thesaid Letters Patent should read as corrected below.

In the heading to the printed specification, lines 3 and 4, for"assignor, bly mesne assignments, to Kerco, Inc. a Corporation dfDelaware" read assigner, by mesne assignment to Kerr ManufacturingCompany) a Corporation of Delaware Signed and sealed this lst day ofAugust 1967.

(SEAL) Attest:

Edward M. Fletcher, J r.

EDWARD J. BRENNER Attesting Officer Commissioner of Patents

1. IN APPARATUS OF THE TYPE DESCRIBED, A SUPPORT, A SLIDE UNIT MOUNTEDFOR REVERSING SLIDING MOVEMENT ON SAID SUPPORT, A LINKAGE TO OPERATESAID SLIDE UNIT AT VARYING SPEEDS IN DIFFERENT PHASES OF SAID MOVEMENT,SAID LINKAGE COMPRISING A PRIMARY ACTUATOR OPERATIVELY ENGAGING SAIDUNIT, SAID ACTUATOR HAVING A PIVOTAL AXIS ON SAID SUPPORT AND HAVING AFIRST PORTION TO ENGAGE AND OPERATE SAID UNIT AT A GIVEN SPEED IN ONE OFSAID PHASES, AND A SECOND OPERATED PORTION TO BE OPERATED, A SECONDARYACTUATOR OPERATIVELY ENGAGING SAID SLIDE UNIT AND HAVING A PIVOTAL AXISON SAID SUPPORT IN PARALLEL BUT TRANSVERSELY SPACED RELATION TO THEPIVOTAL AXIS OF SAID PRIMARY ACTUATOR, SAID SECONDARY ACTUATOR ALSOHAVING A PORTION TO ENGAGE AND OPERATE SAID UNIT AND A FURTHER PORTIONPROVIDING AN OPERATING CONNECTION FOR ACTUATION BY SAID PRIMARYACTUATOR, WHICH FURTHER PORTION IS TRANSVERSELY SPACED FROM THE PIVOTALAXIS OF THE PRIMARY ACTUATOR, THE MOMENT ARM DISTANCE FROM SAID PRIMARYACTUATOR AXIS TO SAID FURTHER PORTION BEING SUBSTANTIALLY DIFFERENT FROMTHE DISTANCE FROM SAID PRIMARY ACTUATOR AXIS TO ITS SAID SECOND OPERATEDPORTION, SAID ACTUATORS THUS COACTING IN OPERATING THE SLIDE UNIT AT ADIFFERENT SPEED IN ANOTHER OF SAID PHASES, AND AN AUTOMATICALLY CYCLINGDRIVE DEVICE ENGAGING SAID PRIMARY ACTUATOR AT SAID SECOND OPERATEDPORTION OF THE LATTER TO PROVIDE REPEATED VARIABLE SPEED MOVEMENT OF THESLIDE UNIT OVER THE DIRECTION OF THE TWO PHASES.